Hydrostatic axial piston motor of bent-axis construction

ABSTRACT

A variable-displacement hydrostatic axial piston motor of bent-axis construction includes a drive shaft, a cylinder drum that pivots in a pivoting plane, and a one-piece port plate nearly symmetrical with a central plane and with two working ports. The motor further includes an adjusting device with an adjusting piston arranged in the port plate, a control valve arranged on the port plate and with a control valve piston, a feedback spring arranged in the port plate and clamped between the adjusting piston and the control valve piston, a counterbalance valve with a counterbalance spool, and two secondary pressure-limiting valves inserted as cartridge-type inserts into the port plate. The counterbalance spool is accommodated in a valve bore in the port plate. The two working ports are situated on the port plate opposite to the first side. The two secondary pressure-limiting valves are arranged on the same side as the port surfaces.

This application claims priority under 35 U.S.C. § 119 to patentapplication no. DE 10 2017 200 244.1, filed on Jan. 10, 2017 in Germany,the disclosure of which is incorporated herein by reference in itsentirety.

BACKGROUND

The disclosure relates to a variable displacement hydrostatic axialpiston motor of bent-axis construction, which comprises a drive shaft, acylinder drum that can be pivoted in a pivoting plane, a one-piece portplate, which has a central plane extending parallel to the pivotingplane and on which there are two working ports with flat port surfaces,one of which is situated on one side of the central plane and the otheris situated at the same distance from the central plane on the otherside of the central plane. For adjustment of the displacement, thehydrostatic axial piston motor has an adjusting device, which comprisesan adjusting piston arranged in a cylindrical receiving space of theport plate, a control valve arranged on a first side of the port plateand having a control valve piston, and a feedback spring, which isarranged in the port plate, is clamped between the adjusting piston andthe control valve piston and is arranged together with the adjustingpiston and the control valve piston on one axis. A counterbalance valvehaving a counterbalance spool is provided, which is intended to reducethe risk of overspeeding and cavitation of the axial piston motor in anopen hydraulic circuit. To limit the pressure, there are furthermore twosecondary pressure-limiting valves, which are inserted as cartridge-typeinserts into the port plate, of which one secondary pressure-limitingvalve is arranged on one side of the central plane and the othersecondary pressure-limiting valve is arranged on the other side. Thesecondary pressure-limiting valves ensure that the pressure is not toohigh when the axial piston motor is operating as a pump, something thatcan occur under a negative load.

A hydrostatic axial piston motor having the above features is known fromdatasheet RE 91616, Edition 05.2016, for example. In this datasheet,pages 27 to 29 show various versions of a hydrostatic axial pistonmotor, the displacement of which can be varied with the aid of anadjusting device. The adjusting piston of the adjusting device is adifferential piston, which is acted upon over an annular surface by thehigh pressure prevailing in a port of the axial piston motor and thelarger piston surface of which delimits an adjusting chamber, which isconnected to the control valve. The control valve piston of the controlvalve is acted upon in one direction by a force which corresponds to thelevel of a control signal and is, for example, the force of anelectro-proportional magnet or a force produced by a control pressureand is acted upon in the opposite direction by the force of a feedbackspring, which is clamped between the control valve piston and theadjusting piston, with the result that the force exerted on the controlvalve piston by the feedback spring depends on the position of theadjusting piston. Depending on the level of the force corresponding tothe control signal, the adjusting piston is thus moved by the controlvalve to a position such that the spring force is equal to the forcespecified by the control signal.

In the case of the automatic high-pressure-dependent adjustmentdiscussed in said datasheet too, the adjusting piston is a differentialpiston, which is acted upon over an annular surface by the high pressureprevailing in a port of the axial piston motor and the larger pistonsurface of which delimits an adjusting chamber, which is connected to acontrol valve. The control valve piston of the control valve is actedupon in one direction by a spring, which is set to a fixed value, theforce of which, which is exerted on the control valve piston, istherefore not dependent on the position of the adjusting piston, and isacted upon in the opposite direction by the high pressure.

A hydrostatic axial piston motor of bent-axis construction withelectro-proportional adjustment of the displacement is known from DE 19653 165 C2. This axial piston motor has an adjusting device whichcomprises an adjusting piston, which is arranged in a cylindricalreceptacle of the port plate and is designed as a differential piston, acontrol valve arranged on a first side of the port plate and having acontrol valve piston, and a feedback spring, which is arranged in theport plate and is clamped between the adjusting piston and the controlvalve piston. The axes of the adjusting piston, the feedback spring andthe valve piston are aligned with one another and are therefore arrangedtogether on one axis. The control valve piston is acted upon in onedirection by the force of the feedback spring and in the oppositedirection by the force of an electro-proportional magnet. In the eventof a non-equilibrium of forces, the control valve piston is moved out ofits central position, in which it shuts off a control valve portconnected to an adjusting chamber with a small positive or negativeoverlap or a zero overlap, with the result that pressure medium is fedto the adjusting chamber at the adjusting piston or displaced from theadjusting chamber, causing the adjusting piston to move and, in theprocess, to change the force exerted by the feedback spring on thecontrol valve piston until an equilibrium of forces is reestablished atthe control valve piston and the control valve piston once again movesinto its central position.

In the case of the versions of a hydrostatic axial piston motor whichare shown on pages 27 and 28 of datasheet RE 91616, Edition 05.2016, abrake valve having a counterbalance valve and two check valvecombinations, each consisting of two check valves, which are arranged ina separate brake valve housing, is attached to the port plate of theaxial piston motor. The secondary pressure-limiting valves are arrangedin the port plate perpendicularly to a central plane of the port plate.

Pages 32 and 33 of datasheet RE 91616, Edition 05.2016 show versions ofa variable-displacement hydrostatic axial piston motor in which theadjusting piston of the adjusting device for the displacement is asynchronizing piston, i.e. a piston which has two effective areas ofequal size. This can be inserted easily into a blind hole in the portplate, wherein two adjusting chambers are formed in front of the twoends of the adjusting piston after the closure of the blind hole. Themanner in which the displacement is adjusted means that there does notappear to be any particular advantage in any position of the controlvalve in relation to the adjusting piston, and therefore there is verygreat freedom in the arrangement of the control valve. These versions ofa hydrostatic axial piston motor have a port plate into which thecounterbalance valve and the two check valve combinations areintegrated.

SUMMARY

It is the underlying object of the disclosure to develop a hydrostaticaxial piston motor of bent-axis construction having a drive shaft,having a cylinder drum that can be pivoted in a pivoting plane, having aone-piece port plate, which has a central plane extending parallel tothe pivoting plane and on which there are two working ports with flatport surfaces, one of which is situated on one side of the central planeand the other is situated at the same distance from the central plane onthe other side of the central plane, having an adjusting device, whichcomprises an adjusting piston arranged in a cylindrical receptacle ofthe port plate, a control valve arranged on a first side of the portplate and having a control valve piston, and a feedback spring, which isarranged in the port plate, is clamped between the adjusting piston andthe control valve piston and is arranged together with the adjustingpiston and the control valve piston on one axis, having a counterbalancevalve, which has a counterbalance spool, and having two secondarypressure-limiting valves, which are inserted as cartridge-type insertsinto the port plate, of which one secondary pressure-limiting valve isarranged on one side of the central plane and the other secondarypressure-limiting valve is arranged on the other side, in such a waythat it is of compact construction and has few sealing locations.

Fundamentally, this object is achieved by virtue of the fact that thecounterbalance spool is integrated into the port plate. According to thedisclosure, this integration is accomplished by virtue of the fact thatthe counterbalance spool is accommodated in a valve bore in the portplate, said valve bore extending perpendicularly to the central plane,that the two working ports are situated on an opposite side of the portplate to the first side and the port surfaces thereof are designed astwo mutually spaced port surfaces, and that the two secondarypressure-limiting valves are arranged on the same side of a third planeas the port surfaces, said plane passing through the axis of the valvebore for the counterbalance spool and extending perpendicularly to theaxis of the adjusting device, and are arranged between the two portsurfaces in a view parallel to the central plane.

Owing to the integration of the counterbalance valve into the portplate, there are no longer any sealing surfaces between the port plateand a separate housing of the counterbalance valve. A compactconstruction is obtained.

Advantageous embodiments of a hydrostatic axial piston motor accordingto the disclosure can be found in the dependent claims.

If the adjusting device comprises a differential piston as an adjustingpiston, then, as is apparent from DE 196 53 165, the piston per se isinserted from one side and a piston rod from the other side into areceiving space of the port plate, and they are connected to one anotherby means of a screw. On the piston insertion side, the receptacle isclosed by means of a cover secured on the port plate. It is thenadvantageous if, in a hydrostatic axial piston motor according to thedisclosure, the port plate has a depression between the two portsurfaces and the cover which closes the receiving space of the portplate for the adjusting piston and hence a pressure space on one side ofthe adjusting piston is arranged in the depression in the port plate.Thus, the cover is not an obstruction during the fastening of lines tothe port surfaces and does not increase the dimensions of the axialpiston motor. Of course, the depression is also advantageous if theadjusting piston is not a differential piston but is inserted into thereceiving space through an opening between the two port surfaces and theopening is closed by means of a cover.

It is known from DE 103 03 487 B4, for example, how the counterbalancespool of the counterbalance valve is incorporated with the aid of fourcheck valves into the respective return line in which the pressuremedium flows back to a tank from the hydraulic motor. It is furthermoreknown that in each case two of these check valves, of which a firstcheck valve, which is arranged between a working port and an inlet ofthe counterbalance valve and blocks flow towards the working port, and asecond check valve, which is arranged between the outlet of thecounterbalance valve and the same working port and opens towards theworking port, can be combined to form a cartridge-type check valveinsert having a central axis. It is also known that the counterbalancespool is assigned just two check valves, of which in each case one isarranged between a working port and an inlet of the counterbalancevalve. The counterbalance spool and the valve bore thereof are then ofmore complex configuration than in the solution with four check valves.

It is advantageous if, in a hydrostatic axial piston motor according tothe disclosure, a check valve, which is arranged between a working portand an inlet of the counterbalance valve and blocks flow towards theworking port, or the cartridge-type check valve insert associated withone working port, is arranged parallel to the axis of the counterbalancespool on one side of the central plane, and a check valve, which isarranged between the other working port and a second inlet of thecounterbalance valve and blocks flow towards the other working port, orthe cartridge-type check valve insert associated with the other workingport, is arranged parallel to the axis of the counterbalance spool onthe other side of the central plane.

It is expedient if the two check valves or the cartridge-type checkvalve inserts are arranged in such a way that both the central axesthereof are in alignment with one another.

The check valves or the two cartridge-type check valve inserts arepreferably arranged on the same side of the third plane as the secondarypressure-limiting valves, although the distance between the check valvesor the cartridge-type check valve inserts and the third plane is lessthan the distance between the secondary pressure-limiting valves and thethird plane.

The cartridge-type check valve inserts and the installation bores in theport plate can remain unchanged relative to already known designs if afirst fluid passage, which extends within the port plate between a portsurface and an installation bore for a check valve cartridge, opens intothe installation bore closer to the central plane than a second fluidpassage, which extends within the port plate between a secondarypressure-limiting valve and the same installation bore, and if the twofluid passages intersect in a projection parallel to the central planeof the port plate and perpendicularly to the axis of the adjustingdevice.

The port plate of a hydrostatic axial piston motor generally has throughholes, through which screws pass, by means of which the port plate isconnected to another housing part of the axial piston motor. The throughholes have a limiting effect on the route of the passages introducedinto the port plate. If the port plate has a first through hole at adistance from the third plane, on the same side as that on which theworking ports are also situated, said through hole being at a certaindistance from the central plane, and a second through hole, the distanceof which from the third plane is less than that of the first throughhole and/or the distance of which from the central plane is greater thanthat of the first through hole, then a first fluid passageadvantageously passes between the first through hole and the secondthrough hole.

The port surfaces preferably lie in a fourth plane, which extendsparallel to the axis of the drive shaft and is perpendicular to thepivoting plane.

The two secondary pressure-limiting valves are preferably arranged withthe valve axes thereof parallel to the central plane.

BRIEF DESCRIPTION OF THE DRAWINGS

An illustrative embodiment of a hydrostatic axial piston motor accordingto the disclosure is shown in the drawings. The disclosure is nowexplained in greater detail with reference to the figures of thesedrawings.

In the drawings:

FIG. 1 shows a side view of the axial piston motor,

FIG. 2 shows a circuit diagram of the axial piston motor including allthe valves present in the illustrative embodiment,

FIG. 3 shows a section through the port plate of the axial piston motorin a central plane, in which the axis of the drive shaft is situated andwhich extends parallel to the pivoting planes of a cylinder drum of theaxial piston motor,

FIG. 4 shows a section along the line IV-IV in FIG. 3,

FIG. 5 shows a side view of the port plate corresponding to FIG. 1,additionally showing concealed contours,

FIG. 6 shows a control unit to be inserted into the port plate, with acontrol valve for a proportionately to a control pressure, and

FIG. 7 shows a partial plan view of the port plate in perspective.

DETAILED DESCRIPTION

The illustrated hydrostatic axial piston motor of bent-axis constructionhas a housing 10 having a pot-type main housing part 11 and having aport plate 12, by means of which the main housing part 11 is closed. Inthe bottom of the main housing part 11 there is a through opening,through which the drive shaft 13 of the axial piston motor passes to theoutside. The axis of the drive shaft 13 is shown in FIG. 1 and isprovided with the reference number 14. It can also be seen from FIG. 1that the free edge of the main housing part lies in a plane 15 which isnot perpendicular to the axis 14 of the drive shaft 13 but slopesslightly relative to said axis. The mounting edge 17 of the port plate12 also lies in this plane when it is secured on the main housing part11. The axial piston motor is a motor with a variable displacement andhas a cylinder drum 16, which can be pivoted in pivoting planes parallelto the plane of the drawing in FIG. 1.

The port plate has two port surfaces 19 and 20, which are designed asSAE port surfaces and in which there are centrally a port opening 21 anda port opening 22, respectively, and, distributed around the portopening, four threaded holes 23. The two port surfaces 19 and 20 lie ina plane 24, which extends parallel to the axis 14 of the drive shaft andperpendicularly to the pivoting planes of the cylinder drum 16 when theport plate 12 is secured on the main housing part 11. Plane 24 isreferred to as the fourth plane in the description above and in thepatent claims. A port surface having a port opening and the threadedholes can also be referred to overall as a working port.

In the circuit diagram shown in FIG. 2, the main housing part 11 and theport plate 12 are symbolized by rectangles drawn in chain-dotted lines.The drive mechanism of the axial piston motor with the cylinder drum 16,which can be pivoted together with a control plate, and with the driveshaft 13 is depicted with corresponding symbols in the main housing part11. In a known manner, the control plate has two control openings, whichoverlap the inner openings 25 and 26 on the port plate 12, wherein,within the port plate 12, a first fluid passage 27 extends between inneropening 25 and the port opening 21 in port surface 19 and a second fluidpassage 28 extends between inner opening 26 and the port opening 22 inport surface 20.

A series of valves is arranged within the port plate 12. Acounterbalance valve 30 having a continuously movable counterbalancespool 31 has two inlets 32 and 33, of which one inlet 32 is connected tothe first fluid passage 27 and the second inlet 33 is connected to thesecond fluid passage 28. An outlet 34 of the counterbalance valve can beconnected via a first check valve 35 to the first fluid passage 27 andvia a second check valve 36 to the second fluid passage 28, whereincheck valve 35 opens towards fluid passage 27 and check valve 36 openstowards fluid passage 28. Arranged in fluid passage 27, between theattachment points of inlet 32 and outlet 34 of the counterbalance valveto said passage, is a check valve 37, which opens from port opening 21towards inner opening 25. Arranged in fluid passage 28, between theattachment points of inlet 33 and outlet 34 of the counterbalance valveto said passage, is a check valve 38, which opens from port opening 22towards inner opening 26.

When there are no further forces acting on the counterbalance spool 31,said spool adopts a spring-centered central position, in which all threeports of the counterbalance valve are shut off. Via a first controlline, a first control surface on the counterbalance spool can besupplied with the pressure prevailing in the segment of the first fluidpassage 27 which is situated between port opening 21 and check valve 37.Via a second control line, a second control surface on thecounterbalance spool can be supplied with the pressure prevailing in thesegment of the first fluid passage 28 which is situated between portopening 22 and check valve 38. If the pressure in said segment of fluidpassage 27 is higher than in said segment of fluid passage 28, thecounterbalance spool 31 is displaced out of the central position intopositions in which inlet 33 is connected to the outlet 34. If thepressure in said segment of fluid passage 28 is higher than in saidsegment of fluid passage 27, the counterbalance spool 31 is displacedout of the central position into positions in which inlet 32 isconnected to the outlet 34. Here, the flow cross section between therespective inlet and the outlet of the counterbalance valve increasescontinuously with increasing travel of the counterbalance spool.

Moreover, a pressure-limiting and anti-cavitation valve 40 and apressure-limiting and anti-cavitation valve 41 are accommodated in theport plate 12, said valves having both a pressure-reducing function anda nonreturn function and being arranged in series and in mirror symmetrywith respect to one another between the segments of fluid passages 27and 28 which are situated between the check valves 37, 38 and the inneropenings 25, 26. By virtue of the pressure-limiting function of onepressure-limiting and anti-cavitation valve and the simultaneousnonreturn function of the other pressure-limiting and anti-cavitationvalve, pressure fluid can thus flow from one fluid passage 27, 28 intothe other fluid passage 28, 27. A feed opening S is connected to theconnecting passage 39 between the two valves 40 and 41. In their“pressure-limiting” function, valves 40 and 41 form “secondary”pressure-limiting valves which, unlike primary pressure-limiting valves,which limit the pump pressure, limit the pressure at a hydraulic motoror, in more general terms, at a hydraulic load.

Moreover, a switching valve 42, which is designed as a hydraulicallyswitched 2/2-way valve, a brake pressure reducing valve 43, which isconnected to the outlets of the switching valve 42, and a shuttle valve44 are accommodated in the port plate 12, said shuttle valve beingconnected by means of a first inlet to the segment of the first fluidpassage 27 which is situated between port opening 21 and check valve 37,being connected by means of a second inlet to the segment of the secondfluid passage 28 which is situated between port opening 22 and checkvalve 38, and being connected by means of its outlet to the inlet of theswitching valve 42. Thus, the respectively higher pressure from saidsegments is available at the inlet of the switching valve 42. Theswitching valve 42 has a shutoff position, which it can adopt under theaction of a spring, and is acted upon in the direction of an openingposition by the pressure at its inlet. In terms of design, the switchingvalve 42 and the brake pressure reducing valve are combined inaccordance with DE 196 42 567 C1, which is also published as U.S. Pat.No. 5,996,616 A with the disclosure of U.S. Pat. No. 5,996,616 Aincorporated herein by reference in its entirety, to form a brakerelease valve 45 with a single valve spool (see FIG. 4).

The port plate 12 furthermore has a circular-cylindrical blind hole 49(see FIG. 3), in which an adjusting piston 51 belonging to an adjustingdevice 50 for the displacement of the axial piston motor is movablyguided, said piston being designed as a differential piston andprojecting by means of a piston rod 52 from the bottom of the blind hole49. By means of the pressure piston 53 and the piston rod 52 of theadjusting piston 50, an annular pressure chamber 54 on the piston rodside and an adjusting chamber 55 of circular cross section on theopposite side from the piston rod are formed within the blind hole 49.The blind hole 49 is closed by a cover 56 screwed to the port plate.

A control valve 60 having a dedicated housing 61 is mounted on the portplate 12. The control valve 60 is a proportional 3/2-way valve, whichhas a pressure port 62, a tank port 63 and an adjusting port 64, whichis connected fluidically to the adjusting chamber 55 via a bore 65 inthe port plate 12 and in the cover 56. The respectively higher pressurefrom the two inner openings 25 and 26 is present at the pressure port 62of the control valve 60 by way of two check valves 66 and 67, which areonce again arranged in the port plate 12. The tank port 63 of thecontrol valve is open towards the housing interior of the axial pistonmotor, in which a tank pressure prevails. Via the two check valves 66and 67, the respectively higher pressure from the two inner openings 25and 26 is also present in the pressure chamber 54 of the adjustingpiston 51.

The control valve piston 70 of the control valve 60 is acted upon by wayof a connection of the adjusting port 64 to the pressure port 62 by acontrol pressure that can be supplied via a control pressure port X ofthe housing 61 and is acted upon by way of a connection of the adjustingport 64 to the tank port 63 by a feedback spring 71 and a return spring72, the force of which is adjustable. The feedback spring 71 is clampedbetween the control valve piston 70 and the piston rod 52 of theadjusting piston 51. The stress of said spring and hence the forceexerted by it on the control valve piston 70 change with the position ofthe adjusting piston 51. Thus, the position of the adjusting piston andhence the position of the cylinder drum 16 are fed back as a force tothe control valve piston 70. This piston thus in each case allowspressure medium to flow to the adjusting chamber 55 or to be displacedfrom the adjusting chamber until the force exerted on it by the springs71 and 72 is exactly the same as the force produced by the controlpressure. Adjustment of the displacement of the axial piston motor inproportion to the control pressure is thus obtained.

The design configuration of the port plate 12 and the arrangement of thevarious valves therein is shown in greater detail in FIGS. 3 to 5, theport plate being in one piece if the adjusting device inserted thereinand the large number of inserted valves are ignored. A central plane 75,which extends parallel to the pivoting planes of the cylinder drum 16and with respect to which the port plate 12 is largely but notcompletely symmetrical, can be seen in FIG. 4. In the central plane, ithas a through hole 76 with an axis 77 which extends parallel to themounting edge 17 and hence to plane 15 and has segments of differentdiameters. This through hole 76 serves to receive the various componentsof the adjusting device 50, of which the adjusting piston 51 with thepressure piston 53 and the piston rod 52 can be seen in the illustrationin FIG. 3. The pressure chamber 54 and the adjusting chamber 55 can beseen, although in FIG. 3 said chamber has not yet been closed by meansof the cover 56. Secured in the piston rod 52 is an adjusting pin 78,which engages in the control plate (not shown specifically). Thefeedback spring 71 is accommodated in a blind hole 79 in the piston rod52 and in segments of the through hole 76 towards which the blind hole79 is open. An adjustable stop disk 80 and a follow-up spring 81 for thestop disk, which are shown in FIG. 6, are furthermore arranged in thesegment of the through hole 76 ahead of the piston rod 52. By adjustingthe stop disk 80, it is possible to set the preload of the return spring72. The through hole 76 is closed on the side opposite the cover 56 byplacing the control valve 60 on the port plate 12.

Design details of the control valve, which is known per se, and of thesprings 71 and 81 can be found in FIG. 6.

It is clearly apparent from FIG. 4 that the counterbalance spool 31 isaccommodated in a valve bore 82 in the port plate 12, said boreextending perpendicularly to the central plane 75. The axis of thecounterbalance spool 31 and the axis of the valve bore 82, whichcoincides with said axis, are denoted by 83. If a plane 84 which passesthrough axis 83 and to which the axis 77 of the through hole 76 isperpendicular is defined, the control valve 60 secured on one side ofthe port plate 12 is situated on one side of this plane 84. Plane 84 isreferred to as the third plane.

The port surfaces 19 and 20 are situated on the opposite side of theport plate 12 from the one on which the control valve 60 is secured. Theplane 24 in which the port surfaces are situated is perpendicular to thecentral plane 75. As can be seen particularly clearly in FIG. 4, the twoport surfaces 19 and 20 are at a distance from one another. Formedbetween them on the port plate 12 is a depression 85, in which the cover56 is situated. As can be seen from FIG. 1, this cover thus projectsonly slightly above the port surfaces. The two pressure-limiting andanti-cavitation valves 40 and 41 are arranged on the same side of plane84 as the port surfaces 19 and 20. The two valves are designed ascartridge-type inserts and are inserted into corresponding installationholes in the port plate 12. In particular, valves 40 and 41 are situatedbetween the two port surfaces 19 and 20, when viewed parallel to thecentral plane 75. The axes 57 and 58 of the installation holes forvalves 40 and 41 and hence also the axes of valves 40 and 41 extendparallel to the central plane 75. In addition, the axes also extendperpendicularly to plane 84. Valve 40 is situated on the same side ofthe central plane 75 as port opening 21, and valve 41 is situated on theother side of the central plane 75, in mirror symmetry with respect tovalve 40.

The two check valves 35 and 37, on the one hand, and the two checkvalves 36 and 38, on the other hand, are combined to form a check valvecartridge 86 and 87, respectively. One check valve cartridge 86 isinstalled from one side and the other check valve cartridge from theopposite side in a through-receptacle 90 of the port plate 12. Thereceptacle 90 is situated in such a way that the axes of the two checkvalve cartridges extend parallel to the axis 83 and are in alignmentwith one another. The distance between the check valve cartridges andplane 84 is less than the distance between valves 40 and 41 and plane84.

A fluid chamber 91 is formed in the central plane 75 in the receptacle90. It is connected by a passage extending in the central plane 75 to afluid chamber 92 of the valve bore 76 for the counterbalance spool 31,said fluid chamber 92 likewise being situated in the central plane 75and forming the outlet of the counterbalance valve 30. In the receptacle90 for the check valve cartridges, fluid chamber 91 is followed on oneside in a direction away from the central plane firstly by a fluidchamber 93 and then a fluid chamber 94. On the other side in a directionaway from the central plane 75, fluid chamber 91 is followed by a fluidchamber 95 and a fluid chamber 96. Arranged between the two fluidchambers 91 and 93 is a closing body 97, which belongs to check valve 35in FIG. 2 and which prevents a flow of pressure medium from fluidchamber 93 into fluid chamber 91 but allows a flow of pressure medium inthe opposite direction. Arranged between the two fluid chambers 93 and94 is a closing body 98, which belongs to check valve 37 in FIG. 2 andwhich prevents a flow of pressure medium from fluid chamber 94 intofluid chamber 93 but allows a flow of pressure medium in the oppositedirection. Arranged between the two fluid chambers 91 and 95 is aclosing body 99, which belongs to check valve 36 in FIG. 2 and whichprevents a flow of pressure medium from fluid chamber 95 into fluidchamber 91 but allows a flow of pressure medium in the oppositedirection. Arranged between the two fluid chambers 95 and 96 is aclosing body 100, which belongs to check valve 38 in FIG. 2 and whichprevents a flow of pressure medium from fluid chamber 96 into fluidchamber 95 but allows a flow of pressure medium in the oppositedirection.

A fluid chamber 101, which is connected to the inner opening 25 andforms inlet 32 of the counterbalance valve 30 is situated in the valvebore 76, at a distance from fluid chamber 92, on one side of the centralplane 75. On the other side of the central plane 75 is a fluid chamber102, which is connected to the inner opening 26 and forms inlet 33 ofthe counterbalance valve 30. In the spring-centered central positionshown in FIG. 4, the counterbalance spool 31 shuts off fluid chambers101 and 102 from fluid chamber 92. During a movement out of the centralposition, the counterbalance spool opens a through flow cross sectionbetween fluid chambers 101 and 92 or between fluid chambers 102 and 92,depending on the direction of motion, while the other fluid chambers ineach case remain shut off from one another.

A fluid passage 110 formed in the port plate 12 leads from port opening21 to the fluid chamber 93 of check valve cartridge 86. In this case,fluid passage 110 extends between two through holes 111 and 112 forfastening screws 115, by means of which the port plate 12 and the mainhousing part 11 are secured on one another. Overall, there are fourthrough holes for fastening screws on each side of the central plane 75,of which through holes there are, in turn, four on one side and four onthe other side of the third plane 84. The through holes extendperpendicularly to plane 15. Through hole 111 is at a shorter distancefrom the central plane 75 than through hole 112 and is at a greaterdistance from the third plane 84 than through hole 112.

The fluid chamber 94 of check valve cartridge 86 is part of a fluidpassage system which extends between check valve 37, pressure-limitingand anti-cavitation valve 40 and inner opening 25 in FIG. 2 and hassegment passages 113 a, 113 b and 113 c. Segment passage 113 a extendsbetween fluid chamber 101 and inner opening 25, segment passage 113 bextends between fluid chamber 101 and fluid chamber 94, and segmentpassage 113 c extends between fluid chamber 94 and pressure-limiting andanti-cavitation valve 40. This segment passage 113 c and fluid passage110 intersect when viewing the port plate in a direction perpendicularto plane 15, as is the case in FIG. 4.

In mirror symmetry with respect to the passages just described, whichare situated on one side of the central plane 75, corresponding passagesare also arranged on the other side of the central plane 75. A fluidpassage 120 formed in the port plate 12 leads from port opening 22 tothe fluid chamber 95 of check valve cartridge 87. In this case, fluidpassage 120 extends between two through holes 121 and 122 for fasteningscrews. Through hole 121 is at a shorter distance from the central plane75 than through hole 122 and at a greater distance from the third plane84 than through hole 122.

The fluid chamber 96 of check valve cartridge 87 is part of a fluidpassage system which extends between check valve 38, pressure-limitingand anti-cavitation valve 41 and inner opening 26 in FIG. 2 and hassegment passages 123 a, 123 b and 123 c. Segment passage 123 a extendsbetween fluid chamber 102 and inner opening 25, segment passage 123 bextends between fluid chamber 102 and fluid chamber 94, and segmentpassage 113 c extends between fluid chamber 96 and pressure-limiting andanti-cavitation valve 41. This segment passage 123 c and fluid passage120 intersect when viewing the port plate in a direction perpendicularto plane 15, as is the case in FIG. 4.

Connecting passage 39 extends between the two pressure-limiting andanti-cavitation valves 40 and 41.

A mode of the hydrostatic axial piston motor in which oil under pressuredelivered by a pump flows to port opening 21 will now be considered. Theoil flows through passage 110 into fluid chamber 93. Pressure builds up,holding closing body 97 on its seat and opening closing body 98. The oilflows via fluid chamber 94, segment passage 113 b, fluid chamber 101 andsegment passage 113 a to inner opening 25, penetrates from there intothe displacement spaces of the cylinder drum 16 and is expelled fromsaid spaces again via inner opening 26. Via segment passage 123 a, theoil flows into fluid chamber 102 and, from there, flows unthrottled intofluid chamber 92 and onward into fluid chamber 91 since thecounterbalance spool 31 has been displaced fully to the right, as viewedin FIG. 4, by the inlet pressure to which the oil flowing to inneropening 25 is subject. The oil flows via closing body 99, which israised from its seat, into fluid chamber 95 and, via passage 120, toport opening 22. Closing body 100 is held on its seat.

If the axial piston motor is now driven externally, e.g. when drivingdownhill, the inlet pressure in passage 110 and in segment passages 113b and 113 a falls. If the inlet pressure falls below the value to whichthe counterbalance valve 30 is set, the counterbalance spool 31 is movedin the direction of the closed central position thereof. As a result,the through flow cross section between fluid chambers 102 and 92 isreduced and the returning oil is built up in segment passage 123 a. Thepressure in segment passage 123 a rises and brakes the motor until thespeed corresponds once again to the inflowing volume flow.

The shuttle valve 44 is inserted into the port plate 12 through a longbore from a side opposite the brake release valve 45.

As can be seen in FIGS. 4 and 7, the two check valves 66 and 67 areinserted into the port plate 12 from the mounting surface 125 for thecontrol valve 60. In FIG. 7, it is also possible to see in the mountingsurface 125 two passages 126 and 127, via which the pressure chamber 54and the adjusting chamber 55 of the adjusting piston 51 are connected tothe control valve 60.

LIST OF REFERENCE SIGNS

-   10 housing-   11 main housing part-   12 port plate-   13 drive shaft-   14 axis of 13-   15 plane-   16 cylinder drum-   17 mounting edge of 12-   19 port surface-   20 port surface-   21 port opening in 19-   22 port opening in 20-   23 threaded holes-   24 fourth plane-   25 inner opening-   26 inner opening-   27 first fluid passage-   28 second fluid passage-   30 counterbalance valve-   31 counterbalance spool-   32 inlet of 30-   33 inlet of 30-   34 outlet of 30-   35 check valve-   36 check valve-   37 check valve-   38 check valve-   39 connecting passage between 40 and 41-   40 pressure-limiting and anti-cavitation valve-   41 pressure-limiting and anti-cavitation valve-   42 switching valve-   43 brake pressure reducing valve-   44 shuttle valve-   45 brake release valve-   49 blind hole-   50 adjusting device-   51 adjusting piston-   52 piston rod-   53 pressure piston-   54 pressure chamber-   55 adjusting chamber-   56 cover-   57 axis of 40-   58 axis of 41-   60 control valve-   61 housing of 60-   62 pressure port of 60-   63 tank port of 60-   64 adjusting port of 60-   65 bore-   66 check valve-   67 check valve-   70 control valve piston-   71 feedback spring-   72 return spring-   75 central plane of 12-   76 through hole in 12-   77 axis of 76-   78 adjusting pin-   79 blind hole in 52-   80 stop disk-   81 follow-up spring-   82 valve bore for 31-   83 axis of 31 and 82-   84 third plane-   85 depression in 12-   86 check valve cartridge-   87 check valve cartridge-   90 receptacle in 12-   91 fluid chamber-   92 fluid chamber in 76-   93 fluid chamber-   94 fluid chamber-   95 fluid chamber-   96 fluid chamber-   97 closing body-   98 closing body-   99 closing body-   100 closing body-   101 fluid chamber-   102 fluid chamber-   110 fluid passage-   111 through hole-   112 through hole-   113 a segment passage-   113 b segment passage-   113 c segment passage-   115 fastening screws-   120 fluid passage-   121 through hole-   122 through hole-   123 a segment passage-   123 b segment passage-   123 c segment passage-   125 mounting surface for 60-   126 hole-   127 hole-   T leakage oil port-   X control port-   S suction port

What is claimed is:
 1. A variable-displacement hydrostatic axial pistonmotor of bent-axis construction, comprising: a drive shaft; a cylinderdrum configured to be pivoted in a pivoting plane; a one-piece portplate, which has a central plane extending parallel to the pivotingplane, and on which there are two working ports with flat port surfaces,of the two working ports, one working port is situated on one side ofthe central plane and the other working port is situated at the samedistance from the central plane on the other side of the central plane;an adjusting device including an adjusting piston arranged in acylindrical receiving space of the port plate; a control valve arrangedon a first side of the port plate and having a control valve piston, afeedback spring arranged in the port plate and clamped between theadjusting piston and the control valve piston, the feedback springarranged together with the adjusting piston and the control valve pistonon one axis; a counterbalance valve having a counterbalance spool; andtwo secondary pressure-limiting valves inserted as cartridge-typeinserts into the port plate, one of the secondary pressure-limitingvalves is arranged on one side of the central plane and the other of thesecondary pressure-limiting valves is arranged on the other side,wherein the counterbalance spool is accommodated in a valve bore in theport plate, the valve bore extending perpendicular to the central plane,wherein the two working ports are situated on an opposite side of theport plate as the first side, and the flat port surfaces are configuredas two mutually spaced port surfaces, and wherein the two secondarypressure-limiting valves are (i) arranged on the same side of a thirdplane as the flat port surfaces, the third plane passing through theaxis of the valve bore for the counterbalance spool and extendingperpendicular to the axis of the adjusting device and (ii) arrangedbetween the two flat port surfaces.
 2. The hydrostatic axial pistonmotor according to claim 1, wherein the port plate has a depressionbetween the two flat port surfaces and wherein a cover secured on theport plate is arranged in the depression, the cover closing thecylindrical receiving space of the port plate for the adjusting pistonand thereby closing a pressure space on one side of the adjustingpiston.
 3. The hydrostatic axial piston motor according to claim 2,wherein the adjusting piston is a differential piston that has effectiveareas of different size.
 4. The hydrostatic axial piston motor accordingto claim 1, further comprising: a first check valve, which is arrangedbetween the one working port and an inlet of the counterbalance valveand blocks flow towards the one working port, is arranged parallel tothe axis of the counterbalance spool on the one side of the centralplane; and a second check valve, which is arranged between the otherworking port and a second inlet of the counterbalance valve and blocksflow towards the other working port, is arranged parallel to the axis ofthe counterbalance spool on the other side of the central plane.
 5. Thehydrostatic axial piston motor according to claim 4, wherein: the firstcheck valve and a third check valve, which is arranged between an outletof the counterbalance valve and the one working port and opens towardsthe one working port, are combined to form a first cartridge-type checkvalve insert having a first central axis, the second check valve and afourth check valve, which is arranged between the outlet of thecounterbalance valve and the other working port and opens towards theother working port, are combined to form a second cartridge-type checkvalve insert having a second central axis, the first cartridge-typecheck valve insert is arranged parallel to the axis of thecounterbalance spool on the one side of the central plane, and thesecond cartridge-type check valve insert is arranged parallel to theaxis of the counterbalance spool on the other side of the central plane.6. The hydrostatic axial piston motor according to claim 4, wherein thefirst check valve and the second check valve each have a longitudinalaxis, and are arranged such that the longitudinal axis of the firstcheck valve is aligned with the longitudinal axis of the second checkvalve.
 7. The hydrostatic axial piston motor according to claim 4,wherein the first check valve and the second check valve are arranged onthe same side of the third plane as the two secondary pressure-limitingvalves, although a distance between the first check valve and the thirdplane and the second check valve and the third plane is less than adistance between the two secondary pressure-limiting valves and thethird plane.
 8. The hydrostatic axial piston motor according to claim 4,wherein: a first fluid passage, which extends between one of the flatport surfaces and an installation bore for the first check valve, opensinto the installation bore closer to the central plane than a secondfluid passage, which extends between one of the secondarypressure-limiting valves and the same installation bore, and the firstfluid passage and the second fluid passage intersect in a projectionparallel to the central plane of the port plate and perpendicular to theaxis of the adjusting device.
 9. The hydrostatic axial piston motoraccording claim 8, wherein: the port plate has a first through hole at adistance from the third plane, on the same side as that on which the twoworking ports are also situated, the first through hole being at acertain distance from the central plane, and a second through hole, oneor more of (i) the distance of the second through hole from the thirdplane is less than that of the first through hole and (ii) the distanceof the second through hole from the central plane is greater than thatof the first through hole, and a fluid passage passes between the firstthrough hole and the second through hole.
 10. The hydrostatic axialpiston motor according to claim 1, wherein the flat port surfaces lie ina fourth plane that extends parallel to the axis of the drive shaft andis perpendicular to the pivoting plane.
 11. The hydrostatic axial pistonmotor according to claim 1, wherein the two secondary pressure-limitingvalves are arranged with the valve axes thereof are parallel to thecentral plane.